EP3368797B1 - Engrenage cylindrique - Google Patents

Engrenage cylindrique Download PDF

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Publication number
EP3368797B1
EP3368797B1 EP16788104.4A EP16788104A EP3368797B1 EP 3368797 B1 EP3368797 B1 EP 3368797B1 EP 16788104 A EP16788104 A EP 16788104A EP 3368797 B1 EP3368797 B1 EP 3368797B1
Authority
EP
European Patent Office
Prior art keywords
spur gear
spur gears
spur
wall
gears
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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Application number
EP16788104.4A
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German (de)
English (en)
Other versions
EP3368797A1 (fr
Inventor
Steffen KÄMMERER
Philipp Zemella
Matthias Rauch
Marco Schneider
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Voith Patent GmbH
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Voith Patent GmbH
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Publication of EP3368797A1 publication Critical patent/EP3368797A1/fr
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/048—Type of gearings to be lubricated, cooled or heated
    • F16H57/0493—Gearings with spur or bevel gears
    • F16H57/0495—Gearings with spur or bevel gears with fixed gear ratio
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/042—Guidance of lubricant
    • F16H57/0421—Guidance of lubricant on or within the casing, e.g. shields or baffles for collecting lubricant, tubes, pipes, grooves, channels or the like
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/042—Guidance of lubricant
    • F16H57/0421—Guidance of lubricant on or within the casing, e.g. shields or baffles for collecting lubricant, tubes, pipes, grooves, channels or the like
    • F16H57/0424—Lubricant guiding means in the wall of or integrated with the casing, e.g. grooves, channels, holes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/042—Guidance of lubricant
    • F16H57/043—Guidance of lubricant within rotary parts, e.g. axial channels or radial openings in shafts
    • F16H57/0431—Means for guiding lubricant directly onto a tooth surface or to foot areas of a gear, e.g. by holes or grooves in a tooth flank
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/0458—Oil-mist or spray lubrication; Means to reduce foam formation
    • F16H57/0461—Means to reduce foam formation

Definitions

  • the present invention relates to a spur gear transmission with at least two toothed spur gears, in detail according to the preamble of claim 1.
  • Spur gears of the generic type are for example from WO 2012/028231 A1 known. Such spur gears are designed, for example, as high-speed gears, such as turbo gears.
  • GB 292 540 A describes gears rotating at high speed in a housing, to which a special guide is assigned to improve the lubrication of the gears.
  • the guide partially surrounds the gears and is at least closed on the underside in such a way that the gears do not protrude from the guide.
  • GB 1 426 352 A describes a lubricating device for gears, in which a partially open inner housing is also provided, which tightly encloses the gears on their underside and on one side.
  • GB 458 379 A discloses an air pump integrated into a transmission.
  • the air pump has guide arcs which enclose the gears on their end faces.
  • US 2014/0054114 A1 discloses a lubricating oil supply for a transmission in which a cover completely encloses the pinion of two spur gears and encloses the other gear of the two spur gears over half the circumference.
  • U.S. 5,950,501 A shows a spur gear, the inner housing of which encloses the spur gears at a certain distance and is evacuated by means of a pump or filled with a gas. There are no merging annular gaps and the spur gears do not protrude from the inner housing.
  • U.S. 2,645,305 A describes a lubricating device for spur gears of a transmission with a lateral shield of the spur gears, which protrudes only over a small part of the outer circumference of the spur gears.
  • EP 2 535 618 A1 discloses spur gears which are enclosed by housings but which do not protrude from the housings.
  • WO 2012/028231 A1 discloses a gear transmission with a shell wall which encloses at least one of two cooperating gears and partially or completely blocks the enclosed interior from the environment. The gears do not protrude from the shell wall.
  • JP 2011-163365 A discloses a gear transmission with an oil passage that partially conforms to the shape of the gears.
  • DE 33 31 131 A1 discloses a double-walled housing of a final drive so that the housing can be connected to a coolant circuit and a cooling jacket in the housing can be achieved.
  • the more heat can be dissipated from the area of the toothing with the lubricant the more lubricant is introduced into the toothing or into the meshing engagement of the toothing.
  • the power loss is also markedly increased as the volume of lubricant that is introduced into the toothing increases. A reduction in the temperature stress on the components by introducing a larger flow of lubricant therefore also means an increase in the power loss.
  • the present invention is therefore based on the object of further developing a spur gear of the type mentioned at the outset in such a way that both a high degree of efficiency and a low temperature load on the components is achieved.
  • a spur gear which can also be referred to as a torque / speed conversion device, in particular a speed / speed conversion device between at least one input and one output shaft, with the features of claim 1.
  • a torque / speed conversion device in particular a speed / speed conversion device between at least one input and one output shaft
  • a spur gear transmission according to the invention has at least two toothed spur gears, the teeth of which are in meshing engagement with one another, the spur gears, in particular the two spur gears, each being rotatable about an axis of rotation.
  • the spur gear has an envelope wall which encloses the spur gears, in particular the at least two intermeshing spur gears, at least partially in the circumferential direction and in the direction of the axes of rotation, the envelope wall having an inner contour which is adapted to the outer diameters of the spur gears in such a way that between the shell wall and the spur gears, in particular the shell wall and the two intermeshing spur gears, result in two mutually merging annular gaps, one annular gap each being arranged at least substantially concentrically to a rotation axis.
  • the spur gear is provided both with a lubrication device which is set up to guide a flow of lubricant into the toothing of the spur gears, and also with a cooling device which is set up to flow a coolant flow through one or more cooling channels running inside the shell wall and / or outside along the envelope wall.
  • a lubrication device which is set up to guide a flow of lubricant into the toothing of the spur gears
  • a cooling device which is set up to flow a coolant flow through one or more cooling channels running inside the shell wall and / or outside along the envelope wall.
  • the flow of lubricant is thus smaller than the flow of coolant, in particular the flow of coolant is a multiple of the flow of lubricant, for example at least twice, five times or ten times.
  • the cooling device comprises a sprinkling device by means of which the coolant flow can be trickled or sprayed onto the shell wall from the outside.
  • the shell wall has webs on its outside which laterally limit a flow path of the coolant flow, specifically laterally in relation to the flow direction of the coolant flow over the outside of the shell wall.
  • these webs can be formed integrally on the shell wall or, according to a second embodiment, can be formed from separate components which are connected to the shell wall. The connection can be made by force fit, form fit or material fit and can be made detachable or non-detachable.
  • the cooling device has at least one, advantageously two, coolant-carrying / coolant-carrying pipe (s) running along the outside of the shell wall, which (each) have a plurality of outlet openings positioned at a distance from one another, around the coolant flow distributed outside on the shell wall to muster.
  • a mass and / or volume flow of the coolant flow of the cooling device and the lubricant flow of the lubricating device can advantageously be set separately from one another and in particular independently of one another, so that each of the two currents can be set with a different constant or controllable value, that is, in particular, a value that can be changed during operation.
  • a different medium than the lubricant is used as the coolant, for example water or a water mixture as the coolant and oil as the lubricant.
  • the coolant flow comprises a first oil volume flow and the lubricant flow comprises a second oil volume flow, which are conveyed from a common oil supply, in particular an oil sump in the spur gear, or from separate oil supplies.
  • the shell wall comprises at least one cooling channel which runs at least partially in the direction of the axes of rotation and / or at an angle, in particular perpendicular thereto, within the shell wall and at least in sections follows the inner contour of the shell wall in its course.
  • the shell wall has a thermally conductive, in particular solid, part forming the inner contour and a heat exchanger connected externally to it or integrally connected thereto, in which the at least one cooling channel is formed.
  • the heat exchanger can be designed, for example, as a plate heat exchanger.
  • Other heat exchanger constructions are possible, for example also a tube bundle heat exchanger.
  • the envelope wall is advantageously integrated on its outside Provided the area overflowed by the coolant flow with a profiled surface.
  • the surface profile can be formed for example by stairs or steps and / or depressions.
  • the coolant flow flows in stages along the stairs on the outside of the shell wall from top to bottom. Steps act like a dam wall, which is flown over when it reaches its apex.
  • coolant flow runs freely into an oil sump positioned below the shell wall, especially in configurations in which the coolant flow is also applied at least to the outside of the shell wall. In principle, however, it is also possible for coolant to flow freely out of the at least one cooling channel in the shell wall into the oil sump.
  • the webs advantageously provided on the envelope wall can, for example, be raised in the radial direction of the axes of rotation relative to an outer surface of the envelope wall overflowing with the coolant flow that they prevent coolant from flowing over end faces of the envelope wall facing in the direction of the axes of rotation. This has the advantage that the coolant cannot get into the rotating areas of the spur gear, which would result in a corresponding power loss.
  • a maintenance opening is provided in an area of an outer surface of the shell wall overflowing with the coolant flow, which is enclosed by the shaft-like side walls protruding from the outer surface in such a way that the coolant flow is prevented from penetrating the maintenance opening through the side walls.
  • the side walls advantageously protrude at least to the top, that is to say the upper outer diameter of the tube.
  • webs are provided on the shell wall, they protrude shaft-like side walls advantageously at least up to the upper end of the webs.
  • the maintenance opening can be closed, in particular by means of a removable or hinged cover.
  • a removable or hinged cover is not mandatory.
  • the cooling device advantageously ensures uniform wetting of the shell wall or at least part of the outer surface of the shell wall with coolant.
  • at least one tube is provided with outlet openings, according to one embodiment, these are at a constant distance from one another, for example between 10 and 40 mm, in particular from 15 to 25 or 20 mm.
  • a possible diameter of the openings is, for example, 3 mm.
  • the distance between the outlet openings and / or the cross section of the outlet openings vary depending on the respective local heat accumulation at the corresponding position on the outside of the envelope wall.
  • the shell wall is made from hollow profiles according to an advantageous embodiment.
  • the cross-sectional area of the at least one cooling channel is advantageously larger than the cross-sectional area of the walls of the shell wall surrounding the at least one cooling channel, that is, greater than the cross-sectional area of the "solid" material of the shell wall.
  • the at least one cooling channel can also connect to a solid area of the shell wall that is comparatively good at conducting heat.
  • the shell wall encloses the two spur gears in the circumferential direction only over part of their circumference, so that part of the outer circumference of the two spur gears or at least one of the two spur gears protrudes outward from the shell wall. This after Part of the circumference protruding outwardly from the shell wall is thus exposed to the surroundings of the shell wall, for example to an interior space of a gear housing of the spur gear. Accordingly, the spur gears are not completely encapsulated as in the prior art mentioned.
  • the part of the circumference protruding outward from the shell wall lies outside a projection surface which is formed by a cross section perpendicular to the axis of rotation of the spur gears through the parts of the shell wall positioned along the outer circumference of the spur gears.
  • the shell wall not only has an opening over the circumference of the spur gears, through which the spur gears are, so to speak, in visual contact with the surroundings of the shell wall, but the spur gears actually protrude from a corresponding opening in the shell wall and protrude beyond this opening.
  • the lower spur gear accordingly protrudes downward beyond a horizontal plane in which the envelope wall extending downward from the upper to the lower spur gear ends.
  • the protruding part of the two spur gears or of the one spur gear is advantageously positioned on the underside of the spur gears, that is, when the spur gear is in operation, in the direction of an oil sump that collects at the bottom of the spur gear due to gravity.
  • the spur gears are advantageously completely enclosed by the envelope wall, in particular over at least the upper half of the circumference of the respective spur gear, the upper half being closed off at the bottom in particular by a horizontal line, that is, the envelope wall ends on its underside in a horizontal plane.
  • the lower spur gear can start at least substantially at the level of its axis of rotation or below it over an arc of at least approximately at least 90 ° be enclosed and the upper spur gear is then advantageously enclosed by the envelope wall by more than 180 °, in particular by essentially 270 °, starting next to the area of engagement of the two gears and continuing upwards over the apex of the upper spur gear to the opposite side and down again at least substantially at the level of the axis of rotation of the upper spur gear.
  • the part of the spur gears protruding downward from the shell wall, and when the spur gears are positioned one above the other, the part of the lower spur gear protruding downward is advantageously positioned freely above an oil sump in the transmission, in particular at a distance from the oil sump or a lower wall of the transmission housing, the distance being advantageous is a multiple of the distance between the shell wall and the enclosed area of the spur gear or gears.
  • the invention can also be used with the corresponding measure in a transmission in which an oil sump is provided outside the transmission housing or a corresponding oil sump can be dispensed with by means of another suitable lubrication.
  • the intermeshing gearwheels are advantageously arranged free of immersion in a liquid level, in particular an oil level or a corresponding liquid or oil supply.
  • the two spur gears are advantageously positioned next to one another with their axes of rotation in the horizontal direction of the spur gear, the axes of rotation extending in particular within a common horizontal plane.
  • the plane is in particular parallel to the surface of an oil sump at the bottom of the spur gear.
  • an arrangement of the axes of rotation in a plane with an inclination with respect to a horizontal plane is also conceivable.
  • the envelope wall advantageously completely encloses the two spur gears over their upper half and part of the lower half beyond, viewed in a cross section through a vertical plane perpendicular to the axes of rotation of the spur gears.
  • the two parts of the envelope extending beyond the upper half can be designed with a tapered cross section, in particular at their free end.
  • the gap or annular gap between the envelope and the outer diameter of the spur gears is tapered, in particular tapered in a wedge shape, at at least one free end of the envelope. This can be provided at a free end or both free ends of the casing.
  • the area of the meshing of the spur gears, in particular on the upper side of the two spur gears, is free from a cover or a corresponding window is provided in the cover for control purposes.
  • the embodiment shown is based on the knowledge that a reduction in power loss can be achieved not only by generating a negative pressure or vacuum in the area of the toothing of the rotating spur gears, but that in practice a thin layer of low-lubricant, in particular low-oil medium, forms around the spur gears, because the lubricant, especially the oil, is thrown outwards by centrifugal force.
  • a layer or stratification is stabilized by the shell wall, it being possible to establish by targeted selection of the thickness of the annular gaps that a comparatively oil-rich medium can be present outside the shell wall, whereas inside the shell wall, that is, in the annular gaps between the spur gears and the shell wall, a low-oil medium is present. This prevents the lubricant-rich medium from reaching the spur gears, which has to be accelerated and thus increases the power consumption of the spur gears, even without complete encapsulation or without applied vacuum.
  • an additional negative pressure is applied in the interior of the gear housing, which encloses the shell wall, that is, that the pressure in the interior is lower than in the vicinity of the gear housing.
  • a negative pressure can be generated, for example, by means of an external or integrated vacuum pump, the suction side of which is connected to the interior.
  • the power loss of the embodiment according to the invention with a partial or complete encapsulation of the spur gears, the latter being discussed below, and additionally pressure-reduced interior of the gear housing With less power loss, because conventionally the lower density of the medium in the gear housing only results in stratification to a lesser extent, as described above, and thus the oil-rich medium can more easily reach the teeth of the spur gears.
  • the envelope wall provided according to the invention the stratification of the media is artificially adjusted and reinforced, even when the pressure in the interior of the gearbox housing is below the ambient pressure.
  • a spur gear is provided with at least two toothed spur gears, the gears of which are in meshing engagement with one another, the two spur gears each being rotatable about an axis of rotation.
  • a cladding wall here which surrounds the two spur gears in the direction of the axes of rotation, the shell wall having an inner contour which is adapted to the outer diameter of the spur gears in such a way that two annular gaps merging into one another result between the shell wall and the spur gears, with one annular gap each being at least essentially concentric is arranged to each one axis of rotation.
  • the shell wall can now completely or only partially enclose the two spur gears in the circumferential direction, the latter according to the embodiment of the invention shown above.
  • the interior of a gear housing, in which the spur gears are arranged together with the shell wall is provided with a pressure that is higher than the ambient pressure, i.e. the pressure in the external environment of the spur gear outside the gear housing is reduced.
  • a distance is provided between the gear housing and part or the entire circumference of the shell wall, which distance is formed by the interior.
  • an air-lubricant mixture in particular an air-oil mixture, the pressure of which is reduced, for example, by an external or integrated vacuum pump.
  • the part of the outer circumference of the two spur gears protruding from the shell wall extends over an arc of 10 ° to 180 °, in particular 90 ° to 180 °, including or excluding the limit values.
  • the part of the spur gears protruding from the shell wall is positioned on the underside of the spur gears, based on the intended use of the spur gear.
  • the annular gaps can, for example, have a thickness of 1 to 10 mm, at least in the part in which the inner contour of the shell wall and the outer diameter of the spur gears are equidistant or concentric to one another. If wedge-shaped tapering of the gap is provided in the free end areas of the shell wall in the circumferential direction radially around the spur gears, the gap thickness in this area is reduced compared to the above-mentioned area or a gap is even avoided.
  • the envelope wall preferably has at least one extension in the axial direction which corresponds to the axial extension of the spur gear that is partially to be enclosed with the formation of an annular gap. An extension beyond this in the axial direction is also conceivable.
  • the envelope wall is at least partially, preferably completely, laterally open.
  • the envelope wall is designed as a wall spaced in the circumferential direction from the outer diameter of the spur gears, i.e. free of side surfaces or side covers, viewed in the axial direction with respect to the spur gear and coupled to the part of the shell wall running in the circumferential direction around the respective spur gear.
  • an at least partially laterally open design of the shell wall it can be formed by a wall region running in the circumferential direction around the respective spur gear and lateral wall regions coupled to this or integrally formed.
  • the lateral wall areas then extend from the wall area running in the circumferential direction around the respective spur gear in the radial direction towards the axis of rotation of the respective spur gear, preferably only over an area in the area of the outer diameter of the respective spur gear.
  • the lateral wall areas are each arranged at a distance from the end faces of the spur gear.
  • the lateral wall areas can be designed in one piece with the wall area running in the circumferential direction around the respective spur gear or as separate components that are connected to this while forming the shell wall.
  • the connection can be made with a force fit, form fit or material fit. In both cases, oil is not routed close to the gearwheel and it is allowed to cross over into the housing.
  • so-called side plates can be provided at a distance in the axial direction from the wall area running in the circumferential direction around the respective spur gear and thus also the spur gears themselves, which are partially enclosed by the shell wall in the circumferential direction, and which are free from a connection or coupling with the in the circumferential direction are around the respective spur gear extending wall area.
  • the task of these side plates is essentially to prevent the transfer of lubricant from the bearing area of the gear wheels into the shell wall, in particular the gap between the gear wheel and shell wall.
  • These side plates are preferably designed in such a way that, viewed in the radial direction of the gearwheel, they also cover the part of the outer circumference of the respective spur gear on its end face that protrudes from the shell wall. If the protruding part is positioned on the underside of the spur gears, this means that the side plate or plates extends further downwards than the shell wall.
  • a side cover covering the end face can be connected to the shell wall on each end face of the spur gears, the side cover also covering, in particular, the part of the outer circumference of the respective spur gear protruding from the shell wall on its face side. If the protruding part is positioned on the underside of the spur gears, this means that the side cover (s) extends further downwards than the envelope wall.
  • each spur gear can have at least one drive shaft or output shaft which is passed through at least one of the side covers.
  • an opening is provided in at least one side cover or in both side covers in the area of the mutual engagement of the teeth of the two spur gears. This can serve, for example, to discharge lubricant from the area of the spur gears enclosed by the shell wall or from the annular gaps.
  • the lubricant for the spur gears can, for example, be injected into the tooth inlet or, preferably, the tooth outlet of the intermeshing teeth.
  • Appropriate nozzles can be provided there for this purpose.
  • the envelope wall is designed to be tapered in a wedge shape in the circumferential direction of the spur gears at at least one circumferential end or at both circumferential ends.
  • the formation of a wedge at the peripheral ends has the effect that the flow of the air-lubricant mixture is diverted away from the toothing of the spur gears in the radial direction. This prevents the medium rich in lubricant from being sucked into the annular gap.
  • the wedges serve as a seal, so to speak, in order to seal the annular gap against the surroundings or against the interior of the gearbox housing.
  • the spur gears generally rotate towards one another in the area of their circumference covered by the shell wall and turn away from one another in the area of the circumference not covered by the shell wall.
  • the thickness of the annular gap is advantageously selected such that a radial velocity component of the medium flowing in the annular gap is reduced.
  • Medium that has already been accelerated in the circumferential direction should have the most constant speed possible due to the shape of the inner contour of the shell wall.
  • the thickness of the annular gaps should not be selected too small, since the relative speeds in the medium increase with decreasing thickness and thus the loss increases.
  • a spur gear can be designed as a two- or multi-shaft spur gear. In the latter case, a plurality of spur gears each rotatable about an axis of rotation is provided. Each of the spur gears meshes with at least one other of the spur gears.
  • the shell wall is designed to run around at least a partial area of each of the spur gears, the axes of rotation of individual or all of the spur gears being arranged in a common parting joint of the gearbox housing.
  • the shell wall extends, viewed in the axial direction, from a first axially outer spur gear around the outer circumference of the spur gear configuration, forming annular gaps between the inner circumference of the shell wall and the individual spur gears to the second, axially outer spur gear.
  • the shell wall can be designed in one or more parts, depending on the gear configuration, the individual shell wall parts being connected to one another in a non-positive, positive or material fit.
  • the shell wall is formed by a multi-part housing, which comprises at least two housing parts, which are arranged at a distance from one another along a theoretical parting line with the formation of a gap and are each mounted separately in / on a gear housing that accommodates the spur gear unit, forming the shell wall functional unit.
  • the housing preferably comprises at least one upper part and one lower part, which in the area of the theoretical parting line are arranged at a distance from one another with the formation of a gap and free from a connection, the theoretical parting line extending partially or completely essentially within one plane, in which one of the two axes of rotation runs or the two axes of rotation run.
  • the spur gears do not run in the oil sump, ie the gear configuration is free of direct contact between the spur gears and the
  • a spur gear unit integrates input and / or output units through connection with the individual shafts connected to the spur gears to form a machine train, forming a geared turbo machine.
  • Steam turbines, gas turbines, expanders and motors can be used as drive units alone or in combination, and compressors and generators are possible as drive units alone or in combination.
  • the geared turbomachines are thus designed as gear compressors or expander systems or a combination of both.
  • a complete geared turbomachine is designed as a string, with the input and output units, in particular steam turbines, gas turbines, expanders as well as motors and compressors interacting with one another in terms of process technology via the transmission, depending on the design of the geared turbomachine.
  • FIG. 1 shows a spur gear with a first spur gear 1 and a second spur gear 2, which are designed for example as helical or double helical spur gears.
  • the teeth of the two spur gears 1, 2 are in meshing engagement with one another, so that the first spur gear 1, when it is above its axis of rotation 3 rotates, drives the second spur gear 2 via its axis of rotation 4 or vice versa.
  • the direction of rotation of the spur gears 1, 2 is indicated by the arrows.
  • a shell wall 5 that closely surrounds the spur gears 1, 2 is provided, but the shell wall 5 only extends over part of the circumference of the two spur gears 1, 2, so that part of the outer circumference of the spur gears 1, 2 opposite an interior 14 of the Gear housing 13 shown here only schematically is exposed.
  • the part of the outer circumference of the two spur gears 1, 2 protrudes from the shell wall 5 on the underside of the spur gears 1, 2.
  • the inner contour of the shell wall 5 with the outer diameters of the spur gears 1, 2 forms two merging annular gaps 6, 7, which apart from the area of the engagement area 15 of the teeth have a constant thickness over the circumference of the spur gears 1, 2.
  • the part of the outer circumference of the two spur gears 1, 2 protruding from the envelope wall 5 extends over an arc of approximately 180 °, the difference to 180 ° being covered by two wedges 16, 17 at the two circumferential ends of the envelope wall 5 is, that is, the envelope wall 5 is designed to be tapered in a wedge shape at its two peripheral ends.
  • this wedge-shaped taper causes a diversion the flow in the radial direction away from the spur gears 1, 2 in the area of the immersion of the spur gears 1, 2 in the shell wall 5.
  • the projection area from which the two spur gears 1, 2 protrude is limited by the dashed line and the shell wall 5 shown in cross section.
  • the shell wall 5 not only has an opening at the bottom through which the spur gears 1, 2 can be seen from the outside, but the outer circumference of the spur gears 1, 2 protrudes from the shell wall 5.
  • a lubricant sump or oil sump can be provided at the bottom in the transmission housing 13, which is not shown in detail here because it is at a corresponding distance from the underside of the spur gears 1, 2.
  • a suction device that is to say a vacuum pump, can be provided, the suction side of which is connected to the interior space 14 in order to suction it.
  • a vacuum pump is shown only schematically and denoted by the reference symbol 18. However, the invention can also be carried out without such a vacuum pump.
  • the enveloping wall 5 thus describes at least one one-part or multi-part wall area which surrounds the spur gears 1, 2 in the circumferential direction at least partially in the circumferential direction while forming a gap.
  • This The wall area is characterized by an axial extent based on the direction of the course of the axis of rotation of the respective spur gear 1, 2 to be enclosed, which corresponds at least to the axial extent of the respective spur gear. Designs with a shell wall 5 protruding in the axial direction are also conceivable and are also necessary if lateral wall areas are provided.
  • the first spur gear 1 has a drive shaft 10 and the second spur gear 2 has an output shaft 11. Both shafts 10, 11 are passed through the side covers 8. In the case of a second spur gear 2 that drives the first spur gear 1, the shafts 10, 11 would be reversed accordingly.
  • An opening 12 is provided in the side cover 8 and in particular also in the side cover 9 in the area of the mutual engagement of the toothings of the two spur gears 1, 2. This is used to discharge coolant.
  • each spur gear 1, 2 has two gears which are positioned next to one another in the axial direction and in particular at a distance from one another in order to form double gearing, in particular double helical gearing.
  • FIG 3 is shown again schematically an embodiment of a spur gear according to the invention according to a preferred embodiment with partial encapsulation.
  • the shell wall 5 encloses the upper half of the two spur gears 1, 2 and thus ends in a horizontal plane running through the axes of rotation 4, 5, see the dashed line.
  • the oil sump 19 is shown schematically at the bottom of the gear housing 13, which encloses the two spur gears 1, 2 and the shell wall 5. It can be seen that the parts 20 of the spur gears 1, 2 protruding from the shell wall 5, that is to say the parts 20 that are below the plane shown by the dashed line, in which the shell wall 5 ends, are positioned, have a distance D from the gear housing 13 and also a distance d from the oil sump 19, the two spur gears 1, 2 being freely positioned in this area opposite the oil sump 19, in particular without the spur gears interposed 1, 2 covering components. In this way, lubricating oil can easily be discharged from the toothings of the spur gears 1, 2 into the oil sump 19, in particular by being sprayed off freely.
  • FIG. 13 is an alternative embodiment shown in a manner similar to that of FIG Figure 3 shown.
  • the spur gears 1, 2 are positioned one above the other.
  • the Figure 3 and refer to the corresponding reference numerals.
  • the upper spur gear, here the second spur gear 2 is three quarters, that is, approximately 270 ° enclosed by the shell wall 5
  • the lower spur gear, here the first spur gear 1 is over a quarter of its circumference, i.e. over approximately 90 ° enclosed by the envelope wall 5.
  • the lower half of the first spur gear 1 protrudes downward from the envelope wall 5, see here again the dashed line which shows the plane in which the envelope wall 5 ends from above.
  • the distances d, D of the lower spur gear 1 to the oil sump 19 or the gear housing 13 are, as in the embodiment according to FIG Figure 3 , again a multiple of the distance between the spur gears 1, 2 and the shell wall 5 in the area of the enclosure or encapsulation.
  • a first oil volume flow for cooling the spur gears 1, 2 is passed through the shell wall 5.
  • This first oil volume flow is denoted by 21.
  • a first oil pump 22, which conveys the oil from the oil sump 19, is indicated schematically for conveying this first oil volume flow 21.
  • the envelope wall 5 can also be cooled by being sprinkled with the first oil volume flow 21.
  • a cooling channel 28 is shown schematically, which runs within the envelope wall 5. As can be seen, the course of the cooling channel 28 follows the course of the inner contour of the shell wall 5, but this is not mandatory. Such a cooling channel 28 could also be completely dispensed with and the coolant could be conducted exclusively along the outer surface of the envelope wall 5.
  • a second oil volume flow 23 is passed into the toothing of the spur gears 1, 2, advantageously into the engagement area 15 of the toothing, for example through one or more openings 12, as shown in FIG Figure 2 is shown.
  • This second oil volume flow 23 is conveyed out of the oil sump 19 by means of a second oil pump 24, for example.
  • a second oil pump 24 for example.
  • another funding or another source can also be considered.
  • the components or features for lubricating the spur gears 1, 2 form a lubricating device 26, whereas the components and features for cooling the shell wall 5 and thus indirectly the spur gears 1, 2 form a cooling device 27.
  • the first oil volume flow 21 and the second oil volume flow 23 can also be conveyed by means of a common oil pump, although in all cases the first oil volume flow 21 is advantageously greater than the second oil volume flow 23, in particular a multiple thereof.
  • the second oil volume flow 23 can advantageously spray freely from the spur gears 1, 2, while the first oil volume flow 21 usually emerges from at least one corresponding opening in the shell wall 5 or, when the shell wall 5 is sprinkled, runs off or drips off the shell wall 5.
  • the spur gears 1, 2, in contrast to direct cooling can be cooled indirectly by heat transfer via the annular gaps 6, 7 into the shell wall 5. This enables a comparatively small volume flow of lubricating oil, here the second volume flow of oil 23, to be conveyed through the annular gaps 6, 7 and / or the engagement area 15 of the toothing, which reduces the losses.
  • cooling of the shell wall 5 by cooling ribs 25 on the outside of the shell wall 5 is also shown schematically.
  • the casing wall 5 shown is designed with an axial extension which corresponds at least to the axial extension of a spur gear 1 or 2, the casing wall 5 being arranged within the extension area of the spur gear 1 or 2 viewed in the axial direction.
  • a lateral protrusion in the axial direction would also be conceivable.
  • the shell wall 5 is arranged at a distance from the outer circumference of the respective spur gear 1 or 2 in the radial direction.
  • the cooling device comprises two coolant-carrying tubes 30 running along the outside of the shell wall 5, which in the embodiment shown face each other in parallel, but this is not mandatory.
  • the tubes 30 advantageously run on both sides approximately radially outside the end faces of the spur gears 1, 2.
  • the tubes 30 have outlet openings 31 via which coolant can be sprayed or trickled onto the outer circumference of the shell wall 5. Due to the arrangement of the tubes 30 and the outlet opening 31, the outer circumference of the shell wall 5 is evenly wetted and the sprayed-on coolant runs along it of the outer circumference from the outside of the shell wall 5, where it absorbs heat from the shell wall 5.
  • webs 29 are provided which prevent this.
  • the webs 29 on the one hand give the shell wall 5 stability and on the other hand represent a barrier for the coolant flowing on the outside of the shell wall 5.
  • the height of the webs 29 is advantageously dimensioned such that they are at least as high as the tubes 30, i.e. up to whose top is enough.
  • a maintenance opening 32 is provided in the casing wall 5, which is enclosed by side walls 33 in such a way that no coolant flowing over the outside of the casing wall 5 can enter the maintenance opening 32.
  • the maintenance opening 32 can, although not shown here, be closable with a cover. However, this is not mandatory.
  • side plates 37 as shielding plates, which are positioned at a distance from the end faces of the spur gears 1, 2, in particular inserted or mounted in the lower housing half.
  • FIGS 9 and 10th show sectional views through the spur gear and in particular the shell wall 5.
  • the webs 29 and the side walls 33 of the maintenance opening 32 can again be seen.
  • the webs 29 can advantageously also protrude radially inward from the envelope wall 5.
  • FIG. 11 a possible design of the outer surface of the shell wall 5 is shown in order to reduce a flow rate of the coolant along the outer surface of the shell wall 5.
  • projections or steps 34 are provided, over which the sprayed-on coolant must flow.
  • the outer surface of the shell wall 5 wetted with the coolant is also designed to be particularly rough, for example with an average roughness R a of 12.5 or more.
  • the envelope wall 5 is formed by one or more hollow profiles 35, each of which has one or more cooling channels 28.
  • a single hollow profile 35 with a single cooling channel 28 can be provided for forming the envelope wall 5, at least the section of the same to be cooled.
  • a hollow profile 35 with several cooling channels, in particular cooling channels directed parallel to one another, can also be used. be provided.
  • several hollow profiles, each with one or more cooling channels, can be joined together to form the envelope wall 5.
  • a heat exchanger In the embodiment according to Figure 12 thus represents the shell wall 5, so to speak, a heat exchanger.
  • a heat exchanger can also be connected to the outside of the shell wall 5 in order to conduct heat to the heat exchanger 36 via a particularly solid part of the shell wall 5 that forms the inner contour and then to dissipate it with the coolant flowing through the cooling channels 28.
  • Figure 14 an embodiment with a three-shaft spur gear, with two spur gears in the form of pinions in engagement with a large gear.
  • the large wheel is formed by the spur gear 2, while the spur gear 1 is formed by a pinion which is in engagement with it.
  • the other spur gear 40 in engagement with the large gear is also designed as a pinion.
  • the pinions can be input or output pinions, or both pinions are driven by the large wheel.
  • the annular gap formed between the outer circumference of the spur gear 40 and the inner circumference of the envelope wall 5 is denoted by 41.
  • the individual spur gears are arranged with their axes of rotation in one plane. The storage can therefore take place in a flat joint of the gearbox housing 13.
  • the shell wall 5 encloses the individual spur gears 1, 2, 40 around a portion of their outer circumference in the circumferential direction in such a way that the pinions and also the large gear protrude from the shell wall 5 when viewed vertically downwards or in the direction of the oil sump 19.
  • the Figure 15 illustrates a development according to an embodiment Figure 14 with axes of rotation of the spur gears of a multi-shaft spur gear arranged in a joint of the housing 13.
  • a further spur gear 42 in the form of an intermediate gear is provided between the spur gear 40 in the form of the pinion and the spur gear 2, which is designed as a large gear.
  • This intermediate gear is preferably coupled to a drive shaft.
  • the two pinions act as an output pinion.
  • Other constellations are conceivable depending on the application.
  • the Figure 16a illustrates a development according to an embodiment Figure 15 , the large wheel viewed in the vertical direction in the installation position opposite the parting line for mounting the spur gears 1, 40, 42 (pinion and intermediate gear) with an offset axis of rotation of the large wheel.
  • the Figure 16b illustrates the use in a geared turbo machine 47 for such a gear design. This integrates input and / or output units into a machine train via the spur gear. Steam turbines, gas turbines, expanders and motors are possible, either alone or in combination, as drive units Compressors and generators are possible individually or in combination as output units.
  • the geared turbomachines are thus designed as gear compressors or expander systems or a combination of both. In the case shown, compressors V1 to V4 coupled to each of the pinion shafts connected to the pinions are provided as output units, while a drive machine 44 drives them via the spur gear 42 in the form of an intermediate gear.
  • the Figure 17 exemplifies a further development of an embodiment according to Figure 14 , in which a further, in the vertical direction to the other spur gears 1, 40 and 2 offset spur gear 45 in the form of a pinion is in engagement with the spur gear 2.
  • the axes of rotation of the individual spur gears are thus arranged in different planes.
  • the shell wall 5 encloses the spur gear train, the outer spur gears, viewed in the axial direction in the installed position, being enclosed by it in the circumferential direction in such a way that a portion of these protrude in the direction of the oil sump 19.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • General Details Of Gearings (AREA)
  • Gear Transmission (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Claims (16)

  1. Engrenage à pignons droits comprenant au moins deux pignons droits dentés (1, 2) dont les dentures sont en prise d'engrènement l'une avec l'autre, et qui peuvent à chaque fois tourner par le biais d'un axe de rotation (3, 4) ;
    1.1 avec une paroi d'enveloppe (5) qui enveloppe les deux pignons droits (1, 2) au moins en partie dans la direction périphérique et dans la direction des axes de rotation (3, 4) ;
    1.2 la paroi d'enveloppe (5) présentant un contour intérieur qui est adapté aux diamètres extérieurs des pignons droits (1, 2) de telle sorte qu'il se forme deux fentes annulaires se prolongeant l'une dans l'autre (6, 7) entre la paroi d'enveloppe (5) et les pignons droits (1, 2), en particulier entre la paroi d'enveloppe (5) et les deux pignons droits en prise l'un avec l'autre, une fente annulaire (6, 7) étant disposée à chaque fois concentriquement par rapport à un axe de rotation respectif (3, 4) ;
    1.3 avec un dispositif de lubrification (26) qui est prévu pour conduire un écoulement de lubrifiant dans les dentures des pignons droits (1, 2) ; et
    1.4 un dispositif de refroidissement (27) étant en outre prévu ;
    caractérisé en ce que
    1.5 le dispositif de refroidissement est prévu pour conduire un écoulement de réfrigérant à travers un ou plusieurs canaux de refroidissement (28) s'étendant à l'intérieur de la paroi d'enveloppe (5) et/ou à l'extérieur le long de la paroi d'enveloppe (5) ;
    1.6 la paroi d'enveloppe (5) comprend une partie thermoconductrice constituant le contour intérieur et un échangeur de chaleur (36) raccordé à celle-ci à l'extérieur ou se raccordant intégralement à celle-ci, dans lequel est réalisé l'au moins un canal de refroidissement (28).
  2. Engrenage à pignons droits selon la revendication 1, caractérisé en ce qu'un débit massique et/ou un débit volumique de l'écoulement de réfrigérant du dispositif de refroidissement (27) et de l'écoulement de lubrifiant du dispositif de lubrification (26) peuvent être ajustés séparément l'un de l'autre et notamment indépendamment l'un de l'autre.
  3. Engrenage à pignons droits selon l'une quelconque des revendications 1 et 2, caractérisé en ce que l'écoulement de réfrigérant comprend un premier débit volumique d'huile (21) et l'écoulement de lubrifiant comprend un deuxième débit volumique d'huile (23) qui sont refoulés depuis une réserve d'huile commune, en particulier un carter d'huile (19) dans l'engrenage à pignons droits ou depuis des réserves d'huile séparées l'une de l'autre.
  4. Engrenage à pignons droits selon l'une quelconque des revendications 1 à 3, caractérisé en ce que la paroi d'enveloppe (5) comprend au moins un canal de refroidissement (28) qui s'étend au moins en partie dans la direction des axes de rotation (3, 4) et/ou suivant un certain angle, en particulier perpendiculairement à ceux-ci, à l'intérieur de la paroi d'enveloppe (5) et dont l'allure suit au moins en partie le contour intérieur de la paroi d'enveloppe (5).
  5. Engrenage à pignons droits selon l'une quelconque des revendications 1 à 4, caractérisé en ce que la partie thermoconductrice constituant le contour intérieur est réalisée sous forme massive.
  6. Engrenage à pignons droits selon l'une quelconque des revendications 1 à 5, caractérisé en ce que l'échangeur de chaleur (36) est réalisé sous forme d'échangeur de chaleur à plaques ou sous forme d'échangeur de chaleur à faisceaux de tubes.
  7. Engrenage à pignons droits selon l'une quelconque des revendications 1 à 6, caractérisé en ce que l'écoulement de réfrigérant s'écoule librement dans un carter d'huile (19) positionné en dessous de la paroi d'enveloppe (5).
  8. Engrenage à pignons droits selon l'une quelconque des revendications 1 à 7, caractérisé en ce que la paroi d'enveloppe (5) entoure les deux pignons droits (1, 2) dans la direction périphérique seulement sur une partie de leur périphérie, de telle sorte qu'une partie de la périphérie extérieure des deux pignons droits (1, 2) ou d'au moins l'un des deux pignons droits (1, 2) fasse saillie vers l'extérieur hors de la paroi d'enveloppe (5), la partie faisant saillie hors de la paroi d'enveloppe (5) des deux pignons droits (1, 2) ou de l'un des pignons droits (1, 2) étant positionnée sur le côté inférieur des pignons droits (1, 2).
  9. Engrenage à pignons droits selon la revendication 8, caractérisé en ce que la partie de la périphérie extérieure des deux pignons droits (1, 2), faisant saillie hors de la paroi d'enveloppe (5) s'étend à chaque fois suivant un arc de 10° à 180°, en particulier de 90° à 180°.
  10. Engrenage à pignons droits selon la revendication 8 ou 9, caractérisé en ce que la paroi d'enveloppe présente une étendue axiale qui correspond au moins à l'étendue axiale du pignon droit devant être au moins en partie entouré ou qui est supérieure à l'étendue axiale du pignon droit.
  11. Engrenage à pignons droits selon l'une quelconque des revendications 8 à 10, caractérisé en ce que la paroi d'enveloppe est exempte de couvercles latéraux disposés dans la direction axiale, lorsque considérés par rapport au pignon droit, et connectés à la partie de la paroi d'enveloppe s'étendant dans la direction périphérique autour du pignon droit respectif ou
    la paroi d'enveloppe est formée par une région de paroi s'étendant dans la direction périphérique autour du pignon droit respectif et par des tôles latérales connectées à celle-ci ou réalisées intégralement et disposées de manière espacée axialement par rapport au pignon droit, la tôle latérale individuelle, vue dans la direction radiale, étant réalisée avec une étendue radiale dans la région du diamètre extérieur du pignon droit respectif.
  12. Engrenage à pignons droits selon l'une quelconque des revendications 8 à 11, caractérisé en ce que les fentes annulaires (6, 7) présentent une épaisseur de 1 à 10 mm.
  13. Engrenage à pignons droits selon l'une quelconque des revendications 8 à 12, caractérisé en ce que la paroi d'enveloppe (5) est réalisée de manière rétrécie en forme de clavette au niveau d'au moins une extrémité périphérique ou au niveau des deux extrémités périphériques dans la direction périphérique des pignons droits (1, 2) et/ou est disposée à faible distance de la denture du pignon droit respectif (1, 2) en tant que région restante de la périphérie couverte par la paroi d'enveloppe (5) .
  14. Engrenage à pignons droits selon l'une quelconque des revendications précédentes, caractérisé en ce que celui-ci comprend une pluralité de pignons droits pouvant chacun tourner autour d'un axe de rotation, chacun des pignons droits étant en prise d'engrènement avec au moins un autre des pignons droits et la paroi d'enveloppe étant réalisée de manière à s'étendre autour d'au moins une région partielle de chacun des pignons droits, les axes de rotation de pignons droits individuels ou de tous les pignons droits étant disposés dans un plan, en particulier d'un joint de séparation commun du boîtier d'engrenage.
  15. Turbomachine à engrenage (47), qui, par le biais d'un engrenage à pignons droits selon l'une quelconque des revendications 1 à 14, intègre des groupes d'entraînement et/ou de prise de force (44, V1, V2, V3, V4) par connexion aux arbres individuels connectés aux pignons droits pour obtenir un train de machines.
  16. Turbomachine à engrenages (47) selon la revendication 15,
    caractérisée en ce que :
    le groupe d'entraînement et/ou de prise de force (V1, V2, V3, V4) connecté à au moins l'un des aux arbres d'entraînement et/ou de prise de force est un élément du groupe comprenant les éléments ci-dessous :
    - un rotor d'un étage d'un compresseur,
    - un rotor d'un étage d'un expanseur.
EP16788104.4A 2015-10-30 2016-10-28 Engrenage cylindrique Active EP3368797B1 (fr)

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DE102015221234.3A DE102015221234A1 (de) 2015-10-30 2015-10-30 Stirnradgetriebe
PCT/EP2016/076006 WO2017072268A1 (fr) 2015-10-30 2016-10-28 Engrenage cylindrique

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CN108351019B (zh) 2021-02-26
DE102015221234A1 (de) 2017-05-04
CN108351019A (zh) 2018-07-31
US10823279B2 (en) 2020-11-03
US20180320779A1 (en) 2018-11-08
JP6743140B2 (ja) 2020-08-19
EP3368797A1 (fr) 2018-09-05
WO2017072268A1 (fr) 2017-05-04

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